CN103526740B - The anti-back-tipping control system of dynamic compaction machinery and method - Google Patents
The anti-back-tipping control system of dynamic compaction machinery and method Download PDFInfo
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- CN103526740B CN103526740B CN201310504970.0A CN201310504970A CN103526740B CN 103526740 B CN103526740 B CN 103526740B CN 201310504970 A CN201310504970 A CN 201310504970A CN 103526740 B CN103526740 B CN 103526740B
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Abstract
The present invention relates to the anti-back-tipping control system of a kind of dynamic compaction machinery and method, comprise strut, guide rod, oil cylinder, spring and hydraulic control device, wherein: the lateral wall of guide rod has limiting section; Strut is a hollow posts with openend and blind end; The blind end of strut is fixedly connected with oil cylinder; Guide rod inserts the cavity of strut from the openend of described strut, and limiting section is positioned at outside strut; Spring housing is contained in outside guide rod, and between limiting section and the openend of strut; In the dynamic compaction machinery course of work, hydraulic control device provides constant pretightning force by oil cylinder for strut, makes different operating mode lower spring be maintained constant pre compressed magnitude.The present invention can make the rebound amount of jib after rammer unhooking minimum, to solve in prior art jib after rammer unhooking and rocks excessive problem.
Description
Technical field
The present invention relates to engineering machinery field, particularly relate to the anti-back-tipping control system of a kind of dynamic compaction machinery and method.
Background technology
At present, as shown in Figure 1, in use, when hammer ram 1 ' breaks off relations, the spring in anti-squat system 2 ' will have certain decrement to dynamic compaction machinery, less than the rebound amount of jib during uncompressed spring.Because the operating angle (operating angle of jib refers to the angle between jib and horizontal plane) of jib 3 ' is a scope, therefore the spring in anti-squat system 2 ' can not ensure certain pretightning force all the time within the scope of the operating angle of jib 3 ', or spring during jib 3 ' work in anti-squat system 2 ' does not have pretightning force at all, after Condition of Sudden Unloading, jib 3 ' will produce and significantly rock and repeatedly shake under the effect of luffing drag-line 4 ' power.
Existing anti-squat system 2 ' can only play the function that jib 3 ' does not turn over afterwards, effectively can not control jib 3 ' and rock.During dynamic compaction machinery construction, jib rocks greatly, makes car load gravity center shift, causes variable-amplitude steel wire rope 6 ' to slide down or raising line 5 ' slides down, increase the danger of construction.Jib 3 ' rocks and causes greatly car load to rock, and operating personnel also can be made to feel very uncomfortable.
Summary of the invention
The object of the invention is to propose the anti-back-tipping control system of a kind of dynamic compaction machinery and method, it can make the rebound amount of jib after rammer unhooking minimum, to solve in prior art jib after rammer unhooking and rocks excessive problem.
For achieving the above object, the invention provides following technical scheme:
The anti-back-tipping control system of a kind of dynamic compaction machinery, it comprises strut, guide rod, oil cylinder, spring and hydraulic control device, wherein: the lateral wall of described guide rod has limiting section; Described strut is a hollow posts with openend and blind end; The blind end of described strut is fixedly connected with described oil cylinder; Described guide rod inserts the cavity of described strut from the openend of described strut, and described limiting section is positioned at outside described strut; Described spring housing is contained in outside described guide rod, and between described limiting section and the openend of described strut; In the dynamic compaction machinery course of work, described hydraulic control device provides constant pretightning force by described oil cylinder for described strut, and under making different operating mode, described spring is maintained constant pre compressed magnitude.
Further, described hydraulic control device comprises reducing valve and equalizing valve, wherein: the oil-out of described reducing valve is connected with the oil-in of described equalizing valve; The oil-out of described equalizing valve is connected with the rodless cavity of described oil cylinder; The pilot pressure hydraulic fluid port of described equalizing valve is for connecting luffing hoist brake pressure oil.
Further, described equalizing valve is one-way balance valve.
Further, be connected with the blind end bolt of described strut bottom the cylinder barrel of described oil cylinder or weld.
Further, described oil cylinder is plunger case.
A kind ofly adopt the anti-hypsokinesis control method of the dynamic compaction machinery of the anti-back-tipping control system of the dynamic compaction machinery in the various embodiments described above, it comprises the following steps: under the state that hammer ram is static, according to the stressing conditions of the jib of dynamic compaction machinery, calculate the constant pretightning force size required for strut in the anti-back-tipping control system of dynamic compaction machinery; According to the described constant pretightning force calculated, regulated the pressure of rodless cavity in oil cylinder by hydraulic control device in the anti-back-tipping control system of dynamic compaction machinery, until oil cylinder for the support force that strut provides be constant pretightning force size.
Further, according to the pre compressed magnitude of spring, calculate the constant pretightning force size required for strut in the anti-back-tipping control system of dynamic compaction machinery.
Further, the computational methods of the reduction length of unhook rear spring comprise the following steps:
1) setup parameter: spring pre compressed magnitude Δ l in the anti-back-tipping control system of dynamic compaction machinery, the decrement Δ l' of bounce-back rear spring, the hinge that the hinge of oil cylinder and turntable is the first hinge, the hinge of guide rod and jib is the second hinge, jib and turntable in the anti-back-tipping control system of dynamic compaction machinery is tri-joint mechanism;
2) image data: the distance s of the first hinge and the second hinge, the spacing b of the second hinge and tri-joint mechanism, the spacing c of the first hinge and tri-joint mechanism, jib length L, the spacing a of jib center of gravity and tri-joint mechanism, the operating angle θ of jib, main chord and lower main chord angle α on jib coxopodite arm, angle β between the line of the first hinge and tri-joint mechanism and horizontal plane, before rammer unhooking and hammer ram remain static under jib gravity G
jib, hammer ram gravity G
hammer ramwith the tensile force f of raising line to jib
raising line;
3) according to following formula:
F
anti-hypsokinesis=k Δ l
R
jib=α cos θ
R
hammer ram=Lcos θ
R
jib=acos θ
G
jibr
jib+ G
hammer ramr
hammer ram+ F
anti-hypsokinesisr
anti-hypsokinesis=F
raising liner
raising line+ F
luffing drag-liner
luffing drag-line
Calculate F
luffing drag-line;
4) according to following formula, P is calculated
static energy:
P
static energy=P
luffing drag-line+ P
raising line+ P
spring+ P
jib
In formula, E is modulus of elasticity, and A is cross-sectional area, and k is rigidity, and F acts on the axial force on luffing drag-line or spring or raising line or jib, and Δ l is stroke or deflection, and l is the length of luffing drag-line or spring or raising line or jib;
5) according to following formula:
Calculate the decrement Δ l' of bounce-back rear spring, the decrement Δ l' of bounce-back rear spring is the function of anti-hypsokinesis spring pre compressed magnitude Δ l;
6) by asking for step 5) in bounce-back rear spring decrement Δ l' minimum value, calculate spring pre compressed magnitude Δ l.
Further, according to the length of different jib, what calculate oil cylinder supplies stroke.
Based on the arbitrary technical scheme in technique scheme, the embodiment of the present invention at least can produce following technique effect:
Because the present invention is provided with strut, guide rod, oil cylinder, spring and hydraulic control device, in the dynamic compaction machinery course of work, hydraulic control device by oil cylinder for strut provides constant pretightning force, make the pre compressed magnitude that the spring under different operating mode is maintained constant, therefore jib plays arm from 0 degree to the first operating angle, spring is uncompressed, and anti-back-tipping control system is zero to jib active force; Jib plays arm from the first operating angle to the second operating angle, spring-compressed, and anti-back-tipping control system has active force to jib, and amount of force is less than the constant pretightning force that the oil cylinder that sets provides as strut; Jib is from the second operating angle to the 3rd operating angle, and by spring-compressed and cylinder piston rod motion, anti-back-tipping control system is always the constant pretightning force that the oil cylinder that sets provides as strut to jib active force; During the bounce-back of rammer unhooking jib, oil cylinder is a rigidity cylinder, the piston rod of oil cylinder keeps original position motionless, jib bounce-back drives guide rod, strut and oil cylinder is acted on by Compress Spring again, thus passive storage power in spring, support reaction is provided to jib, the energy of the storages such as luffing drag-line, jib is absorbed by spring, and effectively control jib by the stroke of spring to swing or vibrations, make the rebound amount of jib after rammer unhooking minimum, to solve in prior art jib after rammer unhooking and rock excessive problem.
Accompanying drawing explanation
Accompanying drawing described herein is used to provide a further understanding of the present invention, and form a application's part, schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 is the structural representation of dynamic compaction machinery in prior art;
Fig. 2 is the part-structure schematic diagram of dynamic compaction machinery provided by the present invention anti-back-tipping control system one embodiment;
Fig. 3 is the decomposing schematic representation of Fig. 2;
Fig. 4 is the principle schematic of hydraulic control device one embodiment in the anti-back-tipping control system of dynamic compaction machinery provided by the present invention;
Fig. 5 is the force analysis schematic diagram of dynamic compaction machinery.
Detailed description of the invention
For making object of the invention process, technical scheme and advantage clearly, below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is further described in more detail.In the accompanying drawings, same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Described embodiment is the present invention's part embodiment, instead of whole embodiments.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.Based on the embodiment in the present invention, those of ordinary skill in the art, not making the every other embodiment obtained under creative work prerequisite, belong to the scope of protection of the invention.Below in conjunction with accompanying drawing, embodiments of the invention are described in detail.
In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end ", " interior ", orientation or the position relationship of the instruction such as " outward " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore limiting the scope of the invention can not be interpreted as.
As in Figure 2-4, the anti-back-tipping control system of dynamic compaction machinery provided by the present invention comprises strut 1, guide rod 2, oil cylinder 3, spring 4 and hydraulic control device 5.Wherein: strut 1 is a hollow cylinder with openend and blind end, the blind end of strut 1 is fixedly connected with bottom the cylinder barrel of oil cylinder 3, and such as the two carries out bolt connection by flange, and the mode of welding also can be adopted to be fixed together.The openend of strut 1 is for inserting guide rod 2.
The lateral wall of one end of guide rod 2 has limiting section 21, and guide rod 2 inserts the cavity of strut 1 from the openend of strut 1, and limiting section 21 is positioned at outside strut 1.The external part of guide rod 2 is connected with the jib 6 of dynamic compaction machinery by bearing pin clamp.Limiting section 21 can be a circle flange, and also can be that interval is arranged and the projection formed a circle, it can be one-body molded with guide rod 2, and it can adopt existing integrated method to obtain, and also can be fixed on the lateral wall of guide rod 2 by the mode of welding.
The piston rod of oil cylinder 3 is connected with the turntable of dynamic compaction machinery by bearing pin clamp.Oil cylinder 3 is as executing agency, and the jib 6 being the dynamic compaction machinery in the course of work by strut 1 and guide rod 2 provides pretightning force and reaction of bearing.In the present embodiment, what oil cylinder 3 adopted is plunger case, but is not limited thereto.
Spring 4 is sleeved on guide rod 2, and between limiting section 21 and the openend of strut 1.Guide rod 2 by the position that spring 4 adjusts in strut 1 provide a larger stroke and and strut 1 interact, Compress Spring 4.4, spring by its elastic deformation for jib 6 provides pretightning force or reaction of bearing.
Carry in hammer or de-hammer process at dynamic compaction machinery, hydraulic control device 5 is by oil cylinder 3 for strut 1 provides constant pretightning force or reaction of bearing, and this active force is delivered to spring 4 and guide rod 2 successively via strut 1, is finally applied on jib 6.By making different operating mode lower spring 4 be maintained constant pre compressed magnitude, thus jib 6 is made to be subject to constant pretightning force.
When the anti-back-tipping control system of dynamic compaction machinery provided by the present invention is assembled, as shown in Figure 5, first, bolt and nut is used to be fixedly connected with bottom the cylinder barrel of oil cylinder 3 with the blind end of strut 1; Then, spring 4 is sleeved on guide rod 2; Afterwards the guide rod 2 being set with spring 4 is fitted together with strut 1, assemble complete.
When the anti-back-tipping control system of dynamic compaction machinery provided by the present invention is assemblied on dynamic compaction machinery, the hinge passed through by the external part of the guide rod 2 of whole anti-squat system on the jib 6 coxopodite arm of bearing pin clamp and dynamic compaction machinery is assembled, then is fitted together by the hinge on the piston rod of oil cylinder 3 and the turntable of dynamic compaction machinery.
As the preferred embodiment of hydraulic control device 5, as shown in Figure 4, hydraulic control device 5 comprises reducing valve 51 and equalizing valve 52, wherein: the oil-out of reducing valve 51 is connected with the oil-in of equalizing valve 52, the oil-out of equalizing valve 52 is connected with the rodless cavity 31 of oil cylinder 3, and reducing valve 51 is used for as oil cylinder 3 provides low pressure oil.What equalizing valve 52 adopted is one-way balance valve, and equalizing valve 52 is as the drainback passage of oil cylinder 3, and its pilot pressure hydraulic fluid port is connected with luffing hoist brake pressure oil, and being used for controlling oil cylinder 3 provides height two-stage reverse back pressure.
The course of work of the present invention is as follows:
(1) carry in hammer process at dynamic compaction machinery, hydraulic control device 5 is low pressure oil supply initiatively, and oil cylinder 3 provides constant pretightning force F
0:
When jib 6 is in 0 degree to the first operating angle θ 1 scope time, guide rod 2 and spring 4 are not all subject to the pressure effect of jib 6, and now oil cylinder 3 does not bear external applied load.High pressure fuel source is after reducing valve 51 reduces pressure, a low pressure oil is provided to oil cylinder 3, the product of the cross-sectional area of the pressure size of low pressure oil and the piston rod of oil cylinder 3 is just in time the size of described constant pretightning force F0, now the piston rod of oil cylinder 3 is overhanging, until to entirely stretching state, that is, the pretightning force size that now oil cylinder 3 provides is F
0.
When jib 6 is in the first operating angle θ 1 to the second operating angle θ 2 scope time, guide rod 2 and spring 4 are all subject to the pressure effect of jib 6, now oil cylinder 3 bears the counter-force effect of spring 4, the elastic force F<F0 of spring 4, and oil cylinder 3 still provides a pretightning force F
0, be in and entirely stretch state.
When jib 6 is in the second operating angle θ 2 to the three operating angle θ 3 scope time, guide rod 2 and spring 4 are all subject to the pressure effect of jib 6, and now oil cylinder 3 bears the counter-force effect of spring 4, the elastic force F=F of spring 4
0, the length of spring 4 remains unchanged, and oil cylinder 3 is also to provide a pretightning force F
0.Now, luffing action done by jib 6, and luffing hoist brake pressure oil acts on the first guide cavity of equalizing valve 52, and equalizing valve 52 is in low reverse backpressure condition.When luffing rises, the piston rod pressurized of oil cylinder 3 is retracted, the fluid of oil cylinder 3 through equalizing valve 52 and reducing valve 51, reverse flow oil sump tank; When luffing falls, hydraulic control device 5 is to oil cylinder 3 fuel feeding, and the piston rod of oil cylinder 3 stretches out, but the length of spring 4 remains unchanged, and the pretightning force of spring 4 remains unchanged, and is still F0.
That is, hammer ram 9 is under non-unhook state, and oil cylinder 3 provides a constant pretightning force F0 to jib 6.
(2) take off in hammer process at dynamic compaction machinery, oil cylinder 3 provides large reaction of bearing:
When luffing action stops, the pressure release of luffing hoist brake, the first guide cavity also pressure release thereupon of equalizing valve 52, equalizing valve 52 is in high oppositely backpressure condition.After unhook, spring 4 one impact compress power given by jib 6, after spring 4 pressurized, power passed to oil cylinder 3.But due to the high back pressure of equalizing valve 52, the fluid that oil cylinder is 3 li can form high pressure, make the power output of oil cylinder 3 become large, the piston rod of final oil cylinder 3 keeps original position motionless, and the active force of jib 6 is absorbed by spring 4 completely.
That is, in hammer ram 9 unhook process, oil cylinder 3 provides a large reaction of bearing close to rigidity to jib 6.
The present invention also can provide a kind of and adopt the anti-hypsokinesis control method of the dynamic compaction machinery of the anti-back-tipping control system of the dynamic compaction machinery in the various embodiments described above, and it comprises the following steps:
Under the state that hammer ram 9 is static, according to the stressing conditions of the jib 6 of dynamic compaction machinery, calculate the constant pretightning force size required for strut 1 in the anti-back-tipping control system of dynamic compaction machinery;
According to the constant pretightning force calculated, regulate rodless cavity hydraulic fluid pressure in oil cylinder 3 by the hydraulic control device 5 in the anti-back-tipping control system of dynamic compaction machinery, until oil cylinder 3 for the support force that strut 1 provides be constant pretightning force size.
The pressure oil that reducing valve 51 exports can enter the rodless cavity of oil cylinder 3 by the one way valve 521 directly in equalizing valve 52, and the piston rod realizing oil cylinder 3 stretches out; When oil cylinder 3 passive compression, pressure oil oppositely flows back to through equalizing valve 52, thus produces reverse back pressure.Pilot pressure hydraulic fluid port due to equalizing valve 52 connects luffing hoist brake pressure oil.When the luffing hoist brake pressure oil of dynamic compaction machinery has pressure, the elevator action of dynamic compaction machinery, now equalizing valve is reverse low back pressure, and oil cylinder 3 can be made to provide pretightning force to remain unchanged for spring 4; When luffing hoist brake pressure oil is without pressure, elevator stops action, and now equalizing valve 5 is reverse high back pressure, and when jib 6 rebounds, the passive pressurized of oil cylinder 3, can produce the large reaction of bearing close to rigidity.
In above-mentioned steps, calculate the constant pretightning force F required for strut 1 in the anti-back-tipping control system of dynamic compaction machinery
0size, specifically comprises:
1) setup parameter: the pre compressed magnitude Δ l of spring 4 in the anti-back-tipping control system of dynamic compaction machinery, the decrement Δ l' of bounce-back rear spring 4, oil cylinder 3 and the hinge of turntable are the first hinge A, guide rod 2 is the second hinge B with the hinge of jib 6 in the anti-back-tipping control system of dynamic compaction machinery, jib 6 is tri-joint mechanism C with the hinge of turntable.
2) image data: the distance s of the first hinge A and the second hinge B, the spacing b of the second hinge B and tri-joint mechanism C, the spacing c of the first hinge A and tri-joint mechanism C, jib 6 length L, the spacing a of jib 6 center of gravity and tri-joint mechanism, the operating angle θ of jib 6, main chord and lower main chord angle α on jib 6 coxopodite arm, angle β between the line of the first hinge and tri-joint mechanism and horizontal plane, hammer ram 9 break off relations front and hammer ram 9 remain static under jib 6 gravity G
jib(G1 in Fig. 5), hammer ram 9 gravity G
hammer ramthe tensile force f of (G2 in Fig. 5) and raising line 8 pairs of jibs 6
raising line.
3) force analysis is carried out to jib 6, according to jib 6 torque equilibrium equation, calculate luffing drag-line 7 power F
luffing drag-line, particularly, according to following formula:
F
anti-hypsokinesis=k Δ l
R
jib=α cos θ
R
hammer ram=Lcos θ
R
jib=acos θ
G
jibr
jib+ G
hammer ramr
hammer ram+ F
anti-hypsokinesisr
anti-hypsokinesis=F
raising liner
raising line+ F
luffing drag-liner
luffing drag-line
Calculate F
luffing drag-line.
Wherein, the angle (180-θ-β-α/2) on the length s on three articles of limits in the triangle surrounded by the first hinge A, the second hinge B and tri-joint mechanism C in Fig. 5, b, c and b and c limit, can in the hope of R
anti-hypsokinesis.
In like manner, according to known triangle sine and cosine theorem and triangle area formula, R can be obtained respectively by the angle of elevator, man-like shelf position and correspondence
raising line, R
luffing drag-line.
4) dynamic compaction machinery is carried in hammer process, luffing drag-line 7, raising line 8, jib 6 and anti-back-tipping control system all store energy, the luffing drag-line 7 (taking off hammer rear) after hammer ram 9 discharges, after the fault offset transfer of raising line 8 and jib 6, energy is all stored on anti-back-tipping control system, carry the jib 6 in hammer process, luffing drag-line 7, raising line 8 all remains static, obtain the energy that the spring 4 in now anti-hypsokinesis system stores, therefore, calculate the pre compressed magnitude of spring 4, namely the energy (the rocking scope of jib 6) stored in dynamic compaction machinery unhook rear defence back-tipping control system is calculated, that passes through rational selection jib again rocks scope, the constant pretightning force size required for the strut in anti-back-tipping control system can be known.The step calculating the reduction length of unhook rear spring 4 is as follows:
(4-1) according to following formula:
P
static energy=P
luffing drag-line+ P
raising line+ P
spring+ P
jib
Above-mentioned various in, E is modulus of elasticity, and A is cross-sectional area, k is rigidity, F acts on the axial force on luffing drag-line or spring or raising line or jib, and Δ l is stroke (or deflection), and l is the length of luffing drag-line or spring or raising line or jib.
Wherein: P
luffing drag-line, P
raising line, P
spring,p
jibp can be adopted
iany expression formula try to achieve.And due to the pre compressed magnitude Δ l of spring 4 be unknown number, therefore P
springfor the function of Δ l, i.e. P
static energyfor the function of Δ l.
(4-2) according to following formula:
By the P that step (4-1) calculates
static energysubstitute in above formula, try to achieve the decrement Δ l' of bounce-back rear spring 4, the decrement Δ l' of the rear spring 4 that therefore rebounds is the function of the pre compressed magnitude Δ l of spring 4.
(4-3) by asking for the minimum value of the decrement Δ l' of bounce-back rear spring in step (4-2), the pre compressed magnitude Δ l of spring 4 is calculated.
(5) according to the pre compressed magnitude Δ l of the spring 4 drawn in step (4-3), formula F is substituted into
springin=k Δ l, calculate the constant pretightning force F required for the strut 1 in the anti-back-tipping control system of dynamic compaction machinery
0.
In above-mentioned steps, because the length L of current jib 6 product is on the market divided into 19m, 22m, 25m etc., if need the horizontal length making jib 6 stretch out, namely jib 6 projection length Lcos θ is in the horizontal plane identical, now need the stroke adjusting oil cylinder 3, namely supply stroke.Therefore, constant pretightning force F is provided at control oil cylinder 3
0under precondition, also need the length L according to different jib 6, what calculate oil cylinder 3 supplies stroke, and control oil cylinder 3 supply stroke.
Finally should be noted that: above embodiment is only in order to illustrate that technical scheme of the present invention is not intended to limit; Although with reference to preferred embodiment to invention has been detailed description, those of ordinary skill in the field are to be understood that: still can modify to the specific embodiment of the present invention or carry out equivalent replacement to portion of techniques feature; And not departing from the spirit of technical solution of the present invention, it all should be encompassed in the middle of the technical scheme scope of request of the present invention protection.
Claims (9)
1. the anti-back-tipping control system of dynamic compaction machinery,
It is characterized in that:
Comprise strut, guide rod, oil cylinder, spring and hydraulic control device, wherein:
The lateral wall of described guide rod has limiting section;
Described strut is a hollow posts with openend and blind end;
The blind end of described strut is fixedly connected with described oil cylinder;
Described guide rod inserts the cavity of described strut from the openend of described strut, and described limiting section is positioned at outside described strut;
Described spring housing is contained in outside described guide rod, and between described limiting section and the openend of described strut;
In the dynamic compaction machinery course of work, described hydraulic control device provides constant pretightning force by described oil cylinder for described strut, and under making different operating mode, described spring is maintained constant pre compressed magnitude.
2. the system as claimed in claim 1,
It is characterized in that:
Described hydraulic control device comprises reducing valve and equalizing valve, wherein:
The oil-out of described reducing valve is connected with the oil-in of described equalizing valve;
The oil-out of described equalizing valve is connected with the rodless cavity of described oil cylinder;
The pilot pressure hydraulic fluid port of described equalizing valve is for connecting luffing hoist brake pressure oil.
3. system as claimed in claim 2,
It is characterized in that:
Described equalizing valve is one-way balance valve.
4. system as claimed in claim 3,
It is characterized in that:
Be connected with the blind end bolt of described strut bottom the cylinder barrel of described oil cylinder or weld.
5. system as claimed in claim 4,
It is characterized in that:
Described oil cylinder is plunger case.
6. adopt the anti-hypsokinesis control method of dynamic compaction machinery of the anti-back-tipping control system of dynamic compaction machinery according to any one of claim 1-5,
It is characterized in that:
Comprise the following steps:
Under the state that hammer ram is static, according to the stressing conditions of the jib of dynamic compaction machinery, calculate the constant pretightning force size required for strut in the anti-back-tipping control system of dynamic compaction machinery;
According to the described constant pretightning force calculated, regulate rodless cavity hydraulic fluid pressure in oil cylinder by hydraulic control device in the anti-back-tipping control system of dynamic compaction machinery, until oil cylinder for the support force that strut provides be constant pretightning force size.
7. method as claimed in claim 6,
It is characterized in that:
According to the pre compressed magnitude of spring, calculate the constant pretightning force size required for strut in the anti-back-tipping control system of dynamic compaction machinery.
8. method as claimed in claim 7,
It is characterized in that:
The computational methods of the reduction length of unhook rear spring comprise the following steps:
1) setup parameter: spring pre compressed magnitude Δ l in the anti-back-tipping control system of dynamic compaction machinery, the decrement Δ l' of bounce-back rear spring, the hinge that the hinge of oil cylinder and turntable is the first hinge, the hinge of guide rod and jib is the second hinge, jib and turntable in the anti-back-tipping control system of dynamic compaction machinery is tri-joint mechanism;
2) image data: the distance s of the first hinge and the second hinge, the spacing b of the second hinge and tri-joint mechanism, the spacing c of the first hinge and tri-joint mechanism, jib length L, the spacing a of jib center of gravity and tri-joint mechanism, the operating angle θ of jib, main chord and lower main chord angle α on jib coxopodite arm, angle β between the line of the first hinge and tri-joint mechanism and horizontal plane, before rammer unhooking and hammer ram remain static under jib gravity G
jib, hammer ram gravity G
hammer ramwith the tensile force f of raising line to jib
raising line;
3) according to following formula:
F
anti-hypsokinesis=k Δ l
R
jib=α cos θ
R
hammer ram=Lcos θ
R
jib=acos θ
G
jibr
jib+ G
hammer ramr
hammer ram+ F
anti-hypsokinesisr
anti-hypsokinesis=F
raising liner
raising line+ F
luffing drag-liner
luffing drag-line
Calculate F
luffing drag-line;
4) according to following formula, P is calculated
static energy:
P
static energy=P
luffing drag-line+ P
raising line+ P
spring+ P
jib
In formula, E is modulus of elasticity, and A is cross-sectional area, and k is rigidity, and F acts on the axial force on luffing drag-line or spring or raising line or jib, and Δ l is stroke or deflection, and l is the length of luffing drag-line or spring or raising line or jib;
5) according to following formula:
Calculate the decrement Δ l' of bounce-back rear spring
,the decrement Δ l' of bounce-back rear spring is the function of anti-hypsokinesis spring pre compressed magnitude Δ l;
6) by asking for step 5) in bounce-back rear spring decrement Δ l' minimum value, calculate spring pre compressed magnitude Δ l.
9. method as claimed in claim 8,
It is characterized in that:
According to the length of different jib, what calculate oil cylinder supplies stroke.
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| CN201310504970.0A Active CN103526740B (en) | 2013-10-24 | 2013-10-24 | The anti-back-tipping control system of dynamic compaction machinery and method |
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Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000017659A (en) * | 1998-07-06 | 2000-01-18 | Hitachi Constr Mach Co Ltd | Vibration working equipment |
| CN102491207B (en) * | 2011-12-20 | 2013-07-24 | 中联重科股份有限公司 | Movable-arm tower crane |
| CN202530437U (en) * | 2012-03-22 | 2012-11-14 | 上海三一科技有限公司 | Anti-retroversion buffering device of dynamic compactor and dynamic compactor comprising same |
| CN202688982U (en) * | 2012-06-05 | 2013-01-23 | 北汽福田汽车股份有限公司 | Vibration reducing system for dynamic compactor and dynamic compactor therewith |
| CN102795563B (en) * | 2012-09-07 | 2014-09-17 | 上海三一科技有限公司 | System and method for preventing boom from backward tilting and crane |
| CN203007923U (en) * | 2012-11-22 | 2013-06-19 | 三一重工股份有限公司 | Dynamic compaction machine |
| CN203603138U (en) * | 2013-10-24 | 2014-05-21 | 徐工集团工程机械股份有限公司 | Anti-back-tilting control system of dynamic compactor |
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